Bearing structure



Deg Z1, 1943. T. G. MYERS ET AL BEARING STRUCTURE Filed Aug. 14, 1939 b i I. a v 57 VII Y 5 Sheets-Sheet 2 INVENTOK5 7720mm 'Myz/zi 7 7%,

- 60/ %ZM AT TO KNEY Dec. 21, 1943. MYE S ETA'L I 2,337,403

BEARING STRUCTURE Filed Aug. 14, 1959 3 Sheets-Sheet 3 INVEN TORS may: Kil 91:76

. 660/ e T f/ay av M AT TO KNEY Patented Dec. 21, 1943 BEARING STRUCTURE Thomas G. Myers and George T. Pflegcr, Los Angeles, Calif., assignors to U. S. Electrical Motors, Inc., Los Angeles, (Built, a corporation of California Application August 14, 1939, Serial No. 290,016

9 Claims. (01. cos-197) This invention relates to anti-friction bearing structures, and particularly for such uses as motor bearings.

Usually such bearings are arranged to be packed with a heavy lubricant, such as grease. These bearing structures, although carefully designed to exclude dust or other harmful foreign matter, yet are subjected to such conditions of operation as to make it necessary to replace the grease packed into the bearing with a fresh supply. This renewal of lubricant is commonly provided by the aid of pressure; intended to force or blow out the old lubricant, and to inject the new lubricant. Often, however, no matter how great care may be exercised, a very substantial portion of the old lubricant isleft, as for example in various recesses and in the spaces between the rolling elements of the bearings.

It is one of the objects of the invention to obviate the possibility of such occurrences, and to ensure that substantially all of the lubricant in the bearing structure may be removed in a convenient manner, without the necessity of disassembling the structure.

It is another object of this invention to improve in general, anti-friction bearings of the type hereinabove referred to.

In some installations, it is desirable to adjust.

the supported shaft in an axial direction, as for example to aline a'rotary pump runner in the pump casing. It is another object of-this invention to make it possible to make such adjustments, and yet to provide for convenient renewal of the lubricant.

This invention possesses many other advantages, and has other objects which may be made more easily apparent from a consideration of several embodiments of the invention. For this purpose there are shown a few forms in the drawings accompanying and forming part of the present specification. These forms, which illustrate the general principles of the invention, will now be described in detail; but it-is to be understood that this detailed description is not to be taken in a limiting sense, since the scope of the invention is best defined by the appended claims.

Referring to the drawings:

Figure 1 is a sectional view of a bearing structure with its associated shaft, incorporating the invention;

Fig. 2 is a sectional view taken along plane 2-2 of Fig. 1;

Fig. 3 is an elevation of an electric motor and a pump in which another form of the invention is incorporated;

Fig. 4 is a sectional view, similar to Fig. 1, showing a modified form of the invention, adapted to be utilized in connection with the apparatus illustrated in Fig. 8.

Figs. 5, 6 and 7 are sectional views of further modifications of the bearing structure.

In the form of the invention illustrated in Figs. 1 and 2, a motor shaft I is indicated having a load driving extension 2. This shaft is shown as supported in a bearing standard 3 which may be formed as a bracket orthe like supported on the main frame of a motor. This bracket supports a ball bearing structure 24. Thus the inner race 4 of the ball bearing structure is shown as accommodated on a reduced portion 5 of the shaft I and abutting the shoulder 6 of the shaft. The outer race 1 of the ball bearing structure 24 is-shown as accommodated in the cylindrical bore 8 formed within the flange 9 of the standard 3.

Provisions are made for forming a lubricant housing or chamber that extends on both sides of the structure 24. Thus for example the standard 3 is provided with'an end wall I0 through which the shaft extension 2 passes. A lubricant retaining washer I I, which may be of felt or the like, is accommodated in a circular groove concentric with the axis of the'shaft I, and engaging the outer periphery of the shaft. In this way a confined chamber I2 is formed to the right of the bearing structure 24.

On the inner side of the standard 3 a cap I3 is provided, to define the left hand portion I4 of the lubricant retaining chamber. This cap I3 may be provided with a plurality of cars I5 (Fig. 2) for accommodating the screws I8 for fastening the cap I3 to the inner surface of the standard 3. These screws I6 pass through appropriate apertures extending through the standard 3 and uniformly spaced around the axis of the shaft I. The cap I3 may also be provided with a lubricant retaining washer I! for confining the grease or other lubricant that may be passed into the chamber I2--I4. The cap I3 is shown as being provided with a projecting flange 2I telescoping into the cylindrical surface 9fo'r accurately centering the cap I3 with respect to the axis of the shaft I. I

The standard 3 is provided with'both inlet an outlet openings to pass grease or other lubricant 3 and 4, provisions are also made for axial adjustment of the motor shaft 21. In this instance the motor 28 is shown as driving a pump runner in a pump casing 29. The motor 28 is provided with the end bracket 30, on which i formed a bearing standard 3 l. A similarly adjustable bearing structure may be provided adjacent the right hand end of the motor 28. The axial adjustment of the shaft 21 is provided so that the pump runner may be accurately centered within its housing.

in communication with the left hand portion l4.: 1

of the lubricant chamber. The inner edge. of. the

cap l3 may form an obstruction to the passage into this space, the inner surface ofcap I3 is shown as provided with recesses 22. In the present instance as many recesses 22 -are shown as there are fastening screws l5, although but one of them cooperates with the opening Hi. 'In this Way irrespective of the particular angular relationshlp of the cap l3 with the standard 3. one or the other of the recesses .22 is inevitably positioned opposite the inlet opening l8. x Furthermore, in order further .to assist the passage of the lubricant to the space I4, the bearing standard. 3 is also provided with a recess 23. The cooperating recesses, 22 andv 23, as shown most clearly in Fig. 1, overlap the upper edge of the outer ball bearing race 1, permitting the grease when passed under pressure through the opening Is, to flow readily into the space l4.

,On the opposite side of thebearing structure 24 and within the bearing standard3 there .is a

lubricant outlet aperture 25.. This lubricant outlet aperture is shown as being closed by headlessscrew 26.

When the bearin structure -'ls first installed,

heavylubricantvsuch as grease may bexpassed.

through the opening I 9', the opening 25 being open s as to permit the airin the lubricant chamber to pass outwardly. After the chamber. I2--|4' is completely filled with-lubricant, the headless screws Hand 26 may bra-applied. In filling chamber 12- with lubricant, this lubricant is passed through the spaces between the rolling elements l8 and forms a lubricant packing for the bearing structure. If it should be desired thereafter to renew the lubricant'after continued use, the headless screws and 26 may be removed, andair pressure or newgrease may be" supplied through opening I9 to force or blow the old lubricant out through the aperture 2!. The openings l9 and being placed on opposite sides of the bearing structure 24, ensure that substantially every last vestige of the used lubricant is forced out. appreciable amount of old lubricant is retained. If for example the apertures 49 and 25 were located on the sam sideof the bearin structure 24, it would be inevitable that some of theold grease or lubricant wouldbe retained in-the various narrow passages between therolling elements .In this way it is assured'that no- Thus in the form of the invention, the antifriction bearing is provided with an inner race 32 abutting a shoulder 33 on the shaft 21. A plurality of nuts 34 are threaded on the end of the shaft 21 and abut the race 32 for holding the race in place; The outer race 35 has an external cylindrical surface adapted to slide within the cylindrical surface 35 formed on the inside of the bearing standard 3|. Th rolling elements such as the balls 31 are inserted between the two races. v

The provisions for axially adjusting the position of the shaft 21 may now be described. This adjustment is provided by sliding the outer race 35 within the bearing standard 3|. The left hand surface of the outer race 35 is arranged to abut a flange 38 formed integrally upon the inner edge of a member 39. This member 39 is threadedinto a threaded end'aperture of the standard 3|. It is apparent that by rotating the member 39, as bythe aid of the square projection 40, the axial position of the flange 38 is correspondingly adjusted. The. outer race 35 is urged strongly against the flange 38 resiliently at all times, as by .the aid offa compression spring 4|. This compression spring surrounds the shaft 21 and engages the right hand surface of the race 35 to urge it. toward the left. The compression spring 4| is confined by a cap 42 fastened as by a pluralitr of screws 43 to the bearing standard 3|. This cap 42 may be provided as in the first form witha lubricant retaining washer 44.

Should it be desired to move the shaft 21 toward the right in an axial direction, the member 39 is threaded inwardly with respect to the hearing standard 3 I. When this takes place-the outer race 35 is positively urged toward the rightby the flange 38, and against the pressure of the spring 4|.

Should it be desired to move the shaft 27 axially toward the left, the member 39 is retracted and the spring 4! is allowed to expand to keep the outer race 35 in contact with the flange 38.

Member 39 has an end wall which forms an enclosure 45 around the ball bearing structure.

Provisions are made as in the firstform to pass lubricant into and out of a lubricant chamber and through the spaces between the balls 31. Furthermore, the inlet and outlet openings for the V a downwardly inclined lubricant inlet opening 46 arranged near the top of the bearin structure.

' A lubricant outlet opening 41 is formed near the The lubricant chamber 96 is conveniently outer race 35.

2",ss'7,=4os

race t'fisatherebyheldincontact'with theshouh formed in this instance by the provision'of lubricant retaining rings 55;56, supporteidby'the These retainers are placed-on onposite sides of the balls-31. "Each of these rings 55 and 56 includes a radial'fiange held-in 'agroove 35 as by 'the-aid-of'the'--split The retainers also have bylinclosely spaced from thebuter Opposite *the cyin the outer race spring "rings 51. drical portions 59 surface of the-inner race 32. 'lindrical portions 58 the inner provided with a plurality of shallow groove's '59. These grooves in cooperation with the 'cylindrical portions 58 restrict free passage of the'lubricant'from'the chamber 96.

In order to ensure into the chamber shaft 21 and of the passageways-are formed in the bearing standard 3|. standards?! isshown as having ing with the inner end'of the opening. "This slot 50 is in constant communication with an 'ajnnular groove '5l formed on the outside'oi'therace 35. Irrespective, therefore, of the relative circumferential standard 3|, nular groove for all :axial positions of the outer race -35, appropriate in the outer race '35- a'nd Thus the bearing lubricant can pass into this an- Communicating with this annular groove 5! is' a radial opening -52 which passes to the right hand side of the bearing structure, into the lubricant chamber 96. The width of the groove 5| andthe length of the slot- 50 are such that they remain in communication for either extreme adjustment of the axial position of the race 35.

The outlet opening 41 is likewise wide enough to stay in constant communication with another annular groove53 formed on the outer urfaceo'f the race '35. Communicating with this groove -is..a radial port '54 passing to the left hand-side of the bearing structure, into the chamber "99. Thus again, when lubricant under pressure is passed through the inletopening 46 it must pass through the intervening spaces between the balls 31 from the right hand side to the left handsid'e of the bearing structure. ous grooves and apertures communication is maintained at all times between the inlet and outlet openings and the lubricant chamber 96.

In both the forms of F'g. 1 and Fig. 4, grooves such as 60 may be provided adjacent the lubricant retaining washers I I, I1 and 44, further to obstruct leakage of lubricant past these washers.

In the form of the invention illustrated in Fig. 4, the compression spring 4| is located within the cap 42, and serves to urge the shaft 21 toward the left. This arrangement however is not essential. For example in the form of Fig. 5, a structure is indicated in which a resilient compression spring is utilized to urge the shaft 9| toward the right.

In this instance the anti-friction bearing structure includes the ball bearings 62 located between the outer race 63 and the inner race 64. The inner race is held on the reduced portion 65 of the shaft 6| as by the aid ofa plurality of nuts 66.

The outer race 63 in this instance is firmly held within a cylindrical recess 66' formed in an axially movable member 61. able member 61 has an outer cylindrical surface 68 slidable within the bearing standard 69. The open right hand end 91 of the member 61 has internal threads in which a retaining ring H is threaded to abut the right hand surface of the outer race 83. The left hand surface of the outer race 32 may be that the lubricant can pas's a slot 50 ooperatposition of the race and the By virtue of the V931.- 1

This axially mov-' r'standard-tr. "-Its requc si'on spring 19.

"quail 6311b fro m i passing t rlz located between -"thes'houlder "18 I anclthe righthand surface of the annular space 19 5 i hand "endbf the {spring -19 abuts "the end *fi'ange 9ljof the standardifl.

- In order to' adiust the axial his orm "of fthe invention, use is =du'eed portion of I standard ts. i

- a d-orthes uarepr ieetiomat.

A pass'ageof the lubricant such as grease groove 89 to the space 99, and to the right of the of the lubricant chamber irrespective of the axial position of the shaft 5 I,

The outlet opening 86 is shown as in communication'with a similar annular groove 9| on the exterior-periphery of the member 61. A radial aperture 92 extends through the member 61 and in communication with an internal groove 93 in' the member "61- 4 56 and 16. "It'is'not essential in this form that all of the space Within the adjustable elements 39 and-61 be filled' with'the lubricant; only the chamber 96 or 99 immediately surrounding the ball bearings 31 and 62, need be packed. The space within member 39 or 61, encompassing the inner chamber 96 or 99, may serve conveniently to collect excess lubricant;

Referring tothe assembly ofF 3 wh1ch shows the motor direct connected-to a centrifugal pump,

- such pumps as commonly made, have a thrust exerted on the shaft by the pump runner tending this forinof the invention to use when the thrust is toward the left, the need for a heavy spring is obviated. I s

If the thrust is such as tendsto move the shaft to theright then the arrangement shown in Fig.5 is the preferred form, as a positive stop is provided against movement of the shaft to the right. Movement in the opposite direction, however, is prevented only by a spring, I9, as before.

Figs. fiend 7 illustrate further modifications of the invention in which the axial position of the shaft maybe adjusted and in which the adjustment is positively maintainedagainstthrust in either'direction. i V The general structure cf the form shown in Fig. 6 is similar to that" shownin Fig. 4. Thus, shaft 21 has the inner race of ananti-friction bearing secured thereQn the outer race 35 of the bearingjbeingslidable within the cylindrical surface 36 formed on the bearingstandard 3I.' An adjustinginemberf39 lthreadedlyl engages an end aperture in the standard 3I. andcarries a flange 38 arranged to abut the left hand surface of the outer race 35,; all as before. In this form however outer race ,35 is urged by fiange 38 against the 'lip IOOof a cap IOI,'adjustably secured to the bearing" standard 3I at the inside end of the cylindrical'surfaceifli by severalscrews, oneof whichis shown at I02 It will be apparent that by suitably rotating member 39, flange 38 will be caused to clamp race 35 against lip I of cap IOI. This holds the bearing as well as shaft 21 against movement in an axial direction, cap I00 serving to preventmovementto the right, member 39 serving to prevent, movement to the left. If it is desired to move shaft 21 to the right, screws I02 .are adjusted to move cap IDI to the right, and member 39 is manipulated to clamp race 35 against lip I00. If it isdesired to move shaft 21 to the left. member 39 isadjusted to move flange 38 to the left, and screws I02'are then manipulated to move cap IIlI to'the lefttobring lip I00 against race 35. At "all times race35 is clamped between member 39 and cap It'll. The provisions for greasing the hearing are the same as those in Fig. 4. Cap IDI may be provided with a lubricant retainer such as felt washerl03, if desired.

Fig. 7 shows a modification of Fig. 5, wherein the bearing is positively secured in adjusted position against movement in either direction. The shaft. 6| carries the inner race'64 of an antiiriction bearing, the :outer race 53 of which is clamped within a cylindrical recess I05 formed in-an axially adjustable member or bearing cage I06. Member I06 is exteriorly threaded, 'soas. to be a'djustably secureddn the threaded bore I01 01' the outside'wall of the bearing standard 69. A shoulder I08 is formed on the inside of cage I06, and a cap I09 secured to the open end of cage I06 as by screws III], is arranged to clamp the outer race 63 against the shoulder I08. The cap IDS is shown as having a, felt washer II I to prevent leakage of grease along shaft 6I,

The arrangement is such that the bearing 6364 and shaft 6| are held against axial movement with respect to cage I06, and further, due to the threaded'engagement between cage I06 and bearing standard 69, against axial movement relative to the bearing standard.

. However, the axial position of the shaft SI, maybe adjusted by rotating cage I06 in the bearing standard 69 by means of the square extension H2. Provisions for greasing the bearing are the-same as in the form of Fig. 5.

What is claimed is:

1. In a device of the character described, an anti-friction bearing structure having an inner and an outer race as well as rolling elements between the races, a'standard for supporting the bearing structure, said outer race being axially movable within said standard, and means forming a lubricant chamber extending on both sides of the bearing structure, said standard having inlet and outlet openings communicating with the chamber and on opposite sides of the bearing structure, said outer race having passages respectively connecting the openings'with the chamber for all adjusted positions of said outer race.

2. In a device of the character described, an anti-friction bearing structure having an inner and-an outer race as Well as rolling elements between the races, a standard for supporting the bearing structure, said outer race having a sliding fit within the standard, means adjustable on the standard for defining a limiting abutment for the outer race, resilient means for urging the outer race against said abutment, and means defining a lubricant chamber enclosing the rolling elements, said standard having openings connecting with the chamber for all adjusted positions of said outer race respectively on opposite sides of the rolling elements.

, 3. In a device of the character described, an

anti-friction bearing structure having an inner and an outer race as well as rolling elements between the races, a standard for supporting the bearing structure, said outer race having a sliding fit within the standard, means adjustable on the standard for defining a limiting abutment for the outer race, resilient means for urging the outer race against said abutment, and means defining a lubricant chamber enclosing the rolling elements, said standard having openings connecting with the chamber respectively on opposite sides of the rolling elements, said outer race having passages in continuous communication withsaid openings to'form ports for the passing of lubricant in and out of the chamber.

' 4. In a device of the character described. an

anti-friction bearing structure having an inner and an outer race as .well as rolling elements between the races, a standard for supporting the bearing structure, a member axially slidable Within the standard and carrying the outer race, said member having an extension out of the standard and providing an abutment limiting inward travel of the member with respect to the standard.

and a spring coiled around the member and Within the standard for urging'said member inwardly.

5. In a device of the character described. an anti-friction bearing structure having an inner and an ouIel race as well as rolling elements bethe axial position of the cap on the standard. said tween the races. a standard for supporting the bearing structure, a member axially slidable within the standard and carrying the outer race, said member having an extension out of the standard and providing an abutment limiting inward travel of the member with respect to the standard, and a spring coiled around the member and within the standard for urging said member inwardly, means defining a lubricant chamber that extends on both sides of the rolling bearing elements, the standard having inlet and outlet openings for lubricant, the outer race and the member having ports for the passage of lubricant through said openings in any adjusted position of the bearing structure.

6. In a device of the character described, an anti-friction bearing structure having an inner and an outer race as well as rolling elements between the races, a standard for supporting the bearing structure, a member axially slidable within the standard and carrying the outer race, said member having an extension out of the standard and providing an abutment limiting inward travel of the member with respect to the standard, and a spring coiled around the member and within the standard for urging said member inwardly, means defining a lubricant chamber that extends on both sides of the rolling bearing elements, the standard having inlet and outlet openings for lubricant, the outer race and the member having ports for the passage of lubricant through said openings in any adjusted position of the bearing structure, said ports being so arranged that the inlet and outlet openings are in communication with the chamber respectively on opposite sides of the bearing structure.

7, In an adjustably mounted bearing structure,

a standard for supporting the bearing structure, said bearing structure being of the anti-friction type and including inner and outer races as well as rolling elements between the races, said stand-' ard having a cavity open at both ends, a cap forming a closure for one end of the cavity and supported by the standard, means for adjusting means including relatively adjustable stops on .the cap and the standard and a resilient member for urging said stops into engagement, the outer race of the bearing structure being supp rted by the cap, a shaft secured to the inner race and extending from the opposite end of the cavity, a shoulder on the cap, and means for maintaining the outer race against the shoulder, whereby the axial position of the bearing as well as pf the shaft is determined by the axial position-of the cap.

8. In a device of the character described, a bearing structure of the anti-friction type and capable of supporting a thrust as well as a radial load, said structure having an inner race and an outer race, a shaft carried by the inner race, a, standard having a through aperture, said outer race being supported for axial adjustment within the aperture, resilient means confined in said aperture for urging the outer race in one direc tion, and means cooperating with the standard on the same side of the bearing structure as the resilient means for limiting the movement 01. the outer race in response to said resilient means, said limiting means being axially adjustable with respect to the bearing structure. a g

9. In a device of the character described, an inner race adapted to be carried by a shaft, an outer race, said races defining an annular space, and rolling elements in said space, said outer race extending in an axial direction with respect to the races, so as to project beyond the rolling elements, said outer race having an aperture communicating with the space on one side of the elements, as well as a circumferentially displaced aperture communicating with the space on the other sideof the elements, said outer race being also provided with a pair of spaced annular exterior grooves, respectively communicating with said apertures.

THOMAS G. MYERS. GEORGE T. PFLEGER 

